Printing scale



5Sheets-Sheet 1 Lawrence 5. WW/iams" INVENTOR ATTORNEYS Dec. 4, 1945. .L s. WILLIAMS PRINTING SCALE Filed July 28, 1941 5 1945- L. s. WILLIAMS 2,390,482

PRINTING SCALE Filed July 28-, 1941 5 Sheets-Sheet 2 Lawrence 5. MY/kbms INV ENTOR ATTORNEYS Dec. 4, 1945.

L. S. WILLIAMS PRINTING SCALE Filed July 28 1941 5 Sheets-Sheet 3 Lawrence 5. W/7//'ams ATTORNEYS Dec. 4, 1945. L. s. WlLLl AMS 2,390,432

PRINTING SCALE Filed July 28 1941 5 Sheets-Sheet 4 Lawrence 5. MOW/27073 INVENTOR ATTORNEYS Dec. 4, 1945. Y L. s. WILLIAMS PRINTING SCALE Filed July 28 1941 5 Sheets-Sheet 5 INVENTOR ATTORNEYS Patented Dec. 4, 1945 PRINTING SCALE Lawrence S. Williams, Toledo, Ohio, assignor to Toledo Scale Company, Toledo, Ohio, a corporation of New Jersey Application July 28, 1941, Serial No. 404,308 (01. 234-54) 2 Claims.

This invention relates to weighing scales of the type which automatically position large sized characters for the printing of weights, and which automatically print such weights in large clear figures, and more particularly to mechanism for controlling the positioning of such characters and the timing of the sequence of positioning and printing operations.

In the construction of printing scales there are several difiiculties which must be overcome in order to construct a scale of high accuracy, great durability and rapid operation. Various types of mechanisms have been devised to set up type characters corresponding to the weights indicated on the scale. Some of these mechanisms have employed a multiplicity of parts, including heavy and bulky members, which have, through necessity, often been moved by auxiliary mechanisms. These auxiliary mechanisms have been necessary due to the fact that it is impossible to move anything but the very lightest members by means of the scale mechanism itself. Any heavy parts attached to such mechanism, because of their inertia and mass, destroy the accuracy of the scale, shorten its serviceable life, and, if these two objections are overcome through the use of auxiliary driving mechanisms, the time necessary to actuate such mechanisms must be added to the weighing time, usually resulting in a printing cycle of lengthy duration and thus cutting down on the number of weighing opera tions which can be carried out on the scale, and

consequently on the scales utility. Other devices 'driven by the scale itself have been employed to position, or to carry into position, the type members for printing the weights. Since these type-carrying members must be kept extremely light, and yet strong enough to overcome the shock of a printing impact, their size is necessarily limited. Since the size must be limited, it has been difilcult to construct such printing members having a suincient number of characters to completely cover the ranges of weights which industry has found desirable.

It is an object of this invention to provide a printing scale capable of printing records in large characters in a short printing cycle.

Another object of this invention is to provide a printing scale in which a portion of the type bearing mechanism is moved into position by the scale itself and another portion moved into position by an auxiliary mechanism.

A further object of this invention is to provide a printing scale having a positive auxiliary mechanism for positioning the scale-set type bearing means and for positioning an auxiliary type bearing means.

I It is still another object of this invention to provide an auxiliary mechanism for timing the movements of the various elements of the mech anism and for controlling the sequence of the type setting and printing operations.

And still another object of this invention is to provide a type-carrying member actuated by the scale mechanism, such member carrying type representing the major divisions of weight and an auxiliary mechanism for positioning such member for printing, for positioning an auxiliary indicia bearing member having characters corresponding to the minor divisions of weight and for the timing and controlling of these positioning operations and of the printing operation.

In my copending application Serial No. 211,221 there is disclosed a printing scale of whi h the present invention is a modification and improvement.

More specific objects and advantages are apparent from the description, in which reference is had to the accompanying drawings illustrating a preferred form of scale embodying the invention.

In the drawings:

Fig. I is a view in elevation of a printing mechanism embodying the invention, certain parts being broken away.

Fig. II is a view in side elevation of the printing mechanism illustrated in Fig. I.

Fig. III is a fragmentary detailed view, on a larger scale, taken on the line IIIIII of Fig. I.

Fig. IV is a fragmentary detailed sectional view, taken on the line IV-IV of Fig. I.

Fig. V is a fragmentary detailed view in perspective of the positioning pawl and associated mechanism.

Fig. VI is a fragmentary plan view of the mechanism shown in Fig.'V, taken on the line VI-VI of Fig. I.

Fig, VII is a detailed plan view of a connecting link taken on the line VII-VII of Fig. I, and shown on a larger scale.

Fig. VIII is a schematic view of the selecting mechanism shown at a position of rest and illustrating a typical wiring diagram for the operation of the mechanism embodying the invention.

Figs. IX, X, In, 1021 and XIII are schematic views of the controlling and selecting mechanisms shown in successive stages in a cycle of operation of the printing mechanism shown in Fi I.

Fig. XIV is a fragmentary detailed view, on

a greatly enlarged scale, of the selecting pawl and of the notches in which it is engaged during operation.

These specific drawings and the specific de- 6 scription that follows merely disclose and illustrate the invention and are not intended to impose limitations upon the claims.

frame I2 located within the head of an automatic scale. The axle I I has affixed to its opposite end I an indicator I3 (Fig. II) which is moved over a chart l4 to visually indicate the weight placed upon the scale. Pinned to the axle I I is a pinion I5, which is rotated by a rack I6 vertically moved by the weight counterbalancing mechanism (not shown).

The disk Ill and indicator I3 are positioned in angular relationship to each other, so that the indicator will point to a value on the dial I4 corresponding to that value on the disk II] which will at that moment be in a printing position. The disk In (Fig. I) carries upon its surface, near its periphery, a series of type characters I1 corresponding to the major divisions of weight; that is tens and hundreds of increments. Corresponding to each of the type characters I1 is a notch 4 I8 cut into the edge of the thin disk.

A vertically depending arm I9 is pivoted in an adjustable eccentric pivot which is mounted in a bracket 2| attached to-the subframe I2. Attached to the lower end of the arm I9 is an arcuate strip 22 which is located in the same vertical plane as the type bearing disk Ill. The arcuate strip 22 has characters 23 on its surface corresponding to the digits of weight increments.

The lower edge of the disk I9 and the arcuate strip 22 pass between a horizontally movable means of toggle links 29. In order to eif ect the printing operation, the rod 28 is moved vertically by a solenoid (not shown) which thus squeezes the abutment 24 and platen 25 together and makes an impression of the type characters I1 and 23 on a card or slip 39, which may be inserted between the ribbon 26 and the disk I6 through a slot 3| in a mechanism-cover 32.

The upper end of the arm I9 (Fig III) has mounted therein a projecting finger 33. The finger 33 extends into the opening between the bifurcated ends of a ratchet lever 34. The ratchet lever 34 is pivoted on an adjustable eccentric 35 mounted on the bracket 2| carried by the subframe I2. Attached to theupper end ofthe lever 34 is a short arcuate ratchet sector 36 which lies behind the disk l9 (Fig. I) and the peripheral surface of which is slightly smaller in radius than that of the disk I0 (Fig. III).

The eccentric 29 (Fig. 111) consists of a'pin 31 which is mounted in a.short eccentrically bored cylinder 38, being held therein by the tension of a spring 39 but free to rotate within the cylinder 38, thus acting as a pivot for the arm I9. The cylinder 38 is rotatablymounted in the bracket 2|, and when rotated, changes the pivot point of the arm I9. The eccentric 35 is similarly constructed acting as a pivot for the ratchet lever 34. Adjustment of the eccentric 20 shifts the pivot point of the arcuate strip 22 horizontally, and the type 23 carried thereby, in angular relation to the type I1 on the disk I0. Vertical adjustment of the eccentric 35 varies the pivotal point of the ratchet lever 34 which adjusts the concentricity of its periphery in relation to the p phery of the disk III.

A motor 40 (Fig. II) is mounted in a bracket 4|. The motor 40, through reduction gearing 42, drives a cam shaft 43 journaled in the bracket 4 I. A compound cam 44 is fixed on the cam shaft 43 and consists of three separate cams 45, 46, 41. The cam 45 '(Fig. I) has a short arcuate cam suriace which, upon rotation of the cam shaft, raises the lower arm of a contact 48. The cam 46 has a three-level periphery on which ride a movable arm 49 of a double contact 59, 5| and the lower arm of a contact 52. The contacts 48, 50, 5| and 52 are mounted in an insulating bracket 53, carried by the motor bracket 4|.

A horizontally disposed arm 54 is pivotally mounted in a lower portion of the insulating bracket 53. The free end of the arm 54 (Figs. I and VII) has a projecting roller 55 mounted therein which rides on the surface of the cam 41. The roller 55 is mounted on a pin 56 which extends through the arm 54 and on which is pivoted a vertically disposed connecting link 51., A spring member 58 is attached to the end of the arm 54 and retains the link 51 on the pin 56.

The motor bracket 4| (Fig. II) is mounted-on the subframe I2 by means of jack-connections 59 which serve both to support the bracket 4|, the motor 49 and its associated gears, cams and and contacts, and to electrically connect the motor 49 into the wiring system of the mechanism. The jacks 59 consist of bifurcated pins 60 which are friction-held within sockets, 6| mounted in a plate 62 attached to the subframe I2. Thus, by removing the link 51 from the pin 56, the motor bracket. unit, including the horizontally disposed arm 54, can be detached asa whole from the mechanism and removed from the scale housing in one assembly. Q

The vertically disposed link 51 (Figs. .Iand III) is pivotally connected atits lower end to a substantially horizontally disposed actuating link 63 which ispivotally mounted on a pin 64 fastened to an ear 65 of the bracket 2|. A bell crank 66 is also pivoted upon the pin 64. The bell crank 66 has a horizontally disposed arm 61, the end of which is turned over horizontally to form a resisting surface for theaction of a spring 68, which is upwardly urged by the counterclockwise rotation of the actuating link 63. The

spring 68 provides a resilient connection between the cam driven linkage 51, 63 and 'the bell crank 66. r

A vertical arm 69 of the bell crank 66 projects above the periphery of the disk I0 and has pivoted,

near its uppermost end, a pawl 18. A spring 1| (Fig. V) is attached to the upper end of the arm 69 and the right-hand end of the pawl 19, and tends to force the latching edge of the pawl 19 downward towards theperipher of the disk III.

A guiding member 12 is adjustably mounted on a projection 13 fromthe bracketll. The projection 13 has a vertical face, in a plane parallel to that of the disk I5, against which the guiding member 12 is fastened. The guiding member 12 has an arcuate slot 14, through which mounting screws 15 pass, which is concentric with the disk III, permitting angular adjustment of the member 12 with relation to the disk II). The guiding member 12 has a lower horizontal arm 16 which extends over the disk I8 and which has an incline projects horizontally from the side of the body of the pawl I and rides on the arm I8 of the guidin: member 12 which holds the pawl away from the edge of the disk I8 against the action of the spring 1| An adjustable bracket I9 is also mounted, by means of the screws I5, on the projection I3 and has anarcuate slot 88, similar to the slot 14 in the member I2. Pivoted on the bracket I9 is a preselecting brake 8|. One end of the brake 8| is connected to the bracket I8 by a spring 82 which tends to rock the brake 8| towards the edge of the disk Ill. The brake 8| has an upwardly inclined surface 83, which rides on the pin I8 and is thus held away from the edge of the disk I 8, and a downwardly extending pawl-like portion 84 which, when forced against the edge of the disk I8, is adapted to act as a brake and dampen the motion of the disk III. The lower edge of the pawl-like portion 84 of the brake 8| may also serve as a reselector when one of the notches IS in the periphery of the disk I 8 is positioned by the weight on the scale so that it is immediately below the edge of the brake 8|.

The latching edge of the pawl Ill (Fig. XIV) has a blunt section which is adapted to engage the notches I8, cut in the periphery of the disk I 0, and a chisel-like section which is adapted to engage sharp teeth 85 of the ratchet sector 36.

A limit dog 86 is mounted on a projection 81 of the bracket 2| and has a lower inclined edge which is adapted to halt the movement of the pawl I0 after the pawl 18 has engaged one of the notches I8 in the disk I0, and thus properly position the disk I8 for printing. The limit dog 88 is adjustable on an arcuate slot concentric with the disk- I8 to permit adjustment of the printing position.

The operation of the pawl and preselector will now be described: When the cam 41 (Fig. I) is rotated by the motor 48, the link 51 is lifted and the bell crank 86 is swung in a counterclockwise direction. Movement of the vertical arm 69 of the bell crank 86 in such counterclockwise direction (Fig. V) moves the pawl I8 toward the left and the pin I8 slides down the incline 'II, permitting the latching edge of the pawl 18 to engage the peripher of the disk II]. If one of the notches I8 is not immediately below the latching edge of the pawl 10, the pawl slides along the peripher of the disk I8 until it engages one of the notches I8. Since the arc of the ratchet sector 36 is of a smaller radius than the disk III, the latching edge of the pawl I0 does not engage the teeth 85 until it has fallen into a notch I8. At the same time, the pin I8, having been removed from beneath the upwardly inclined surface 83 of the preselecting brake 8|, the pawl-like portion 84 has been urged downwardly by the spring 82 and is in frictional contact with the edge of the disk I 0 slightly before the edge of the pawl III makes contact therewith, serving to dampen its oscillations so that the latching edge of the pawl I8 can more quickly be engaged in the notch I8. The spring 82 on the preselecting brake 8| has a greater tension than the spring II of the pawl I0, and thus the sliding of the pawl I8 along the edge of the disk I0 cannot move the disk I0 against the b aking effect of the preselecting brake 8 I. After engagement of the pawl I8 in the notch I8 and one of the teeth 85, it continues to move in a counterclockwise direction, carrying the disk I8 and the ratchet sector 38 with it, until its upper edge strikes the limit dog 86, at which time the figures corresponding to the notches entered are In the proper position to be printed.

At certain positions of the disk III, the latching edge of the pawl 18 might strike squarely on a corner of one of the notches I8. This, of course, would not only injure the mechanism but would result in appreciable error since having hit the corner of the notch the pawl I8 might either drop back into the notch or might move forward (to the left Fig. V) to the next notch. In order to prevent the pawl I8 from hitting the corner of the notch I8, the pawl-like portion 84 of the preselecting brake 8| swings down andengages the edge of the disk I0 an instant before the pawl I0 comes into engagement with the disk In and, if it strikes the inclined wall of the notch I8, moves the disk III in a clockwise direction surficiently to assure the landing of the pawl Ill beyond the corner of the notch I8. The adjustment of the guiding member I2 and the bracket I8 determines the relative distance between the landing points of the pawl I0 and the preselecting brake 8| on the disk Ill, and thus determines the distance beyond the edge of the notch I8 at which the pawl I0 will be permitted to land.

The ratchet sector 36, which is attached to the upper end of the ratchet lever 34, has a suflicient number of teeth to represent the digit divisions of weight increment for which there are characters 23 on the arcuate strip 22. These teeth evenly divide the distance between two of the notches I8. The ratchet lever 34 is always in the same position when the scale is at zero, and remains in that position until the sharp portion of the latching edge of the pawl I0 engages one of the teeth 85 and moves the ratchet lever 34 in a counterclockwise direction. Since the arm I 8 (Fig. I), as has been described, is pivotally connected to the ratchet lever 34,'it is pivoted about the eccentric 28 in a counterclockwise direction and the arcuate strip 22 is swung thereby. The relationship between the position of the ratchet lever 34, the ratchet sector 36 and its teeth 85 with respect to the pawl III and associated mechanism, is adjustable by means of a stop screw 88 (Fig. I) mounted in an ear on the bracket 2|. Moving the screw 88 adjusts the rest position of these associated parts.

If the weight on the scale is in even tens of increments, one of the notches I8 will be positioned at th landing point of the pawl I0 which is also the correct position for the first of the teeth 85. In this case, the pawl I0 will immediately drop into the notch I8, engage the first of the teeth 85, and, continuing its counterclockwise movement, will position the type on the disk I0 corresponding to the notch I8, into which it has dropped, and will swing the arcuate strip 22 through its complete length because of the fact that the first tooth 85 of the ratchet sector 38 has been engaged and thus the ratchet lever 34 is moved through its maximum angular movement and the 0 character 23 will be printed.

If, however, the weight on the scale is not in even tens of increments, the notch I8 will not be positioned immediately at the landing point of the pawl I0 and th pawl III will slide along the periphery of the disk It) until it reaches another notch I8 before it engages one of the teeth 85 of the ratchet sector 36. Before the pawl I8 engages a tooth 85, it will have passed over the number of teeth less-one corresponding to the digit which it is desired to select (for example, if the weight ends in 7, the pawl will have passed over six teeth and will have engaged the seventh,

counting from the right in Fig-Y). This will then leave a suflicient distance between the position of the pawl at engagement with the seventh tooth 85 and the limit dog 86, to move th ratchet sector 36, the ratchet lever 34 and the arm I9 a sufiicient distance to swing the 7 character 23 into printing position.

If the weight on the scale, for example, is not in even units of weight, and amounts to approximately 9 /2 of such units of weight, the preselector brake 8| is used to properly position the disk I 9. If the weight on the scale amounts to slightly less than 9 units of weight, a. notch I8 will be located beneath the portion 84 of the preselecting brake 8|, and the contacting edge of the portion 84 will engage the sloping shoulder of the notch I8 and back up the disk I9 in a counterclockwise direction so that the engaging edg of the pawl 19 will contact the edge of the disk I9 just beyond the edge of the notch I8 corresponding to 10 units of weight (this engagement is illustrated in Figs. IX and X). If, on the other hand, the weight on the scale amounts to slightly more than 9 units of weight, the preselecting brake 8I and pawl 19 are so positioned that the edge of the portion 84 will contact the disk I9 just in back of the sloping shoulder of the notch I8 and the engaging edge of the pawl 19 will contact the disk I9 on the sloping shoulder of the notch I8, corresponding to 10 units of weight, and move forward slightly to drop into such notch.

Referring now to Fig. VIII, the selecting mechanism is shown in the rest position The contact 48 is normally open, the contact 59 is normally closed and the contacts 5| and 52 are both normally open.

Power is introduced into the wiring circuit from the power line 89 through a master switch 99 and fuses 9|. One side of the power line leads through the lead line 92 to one side of the motor 49 and to a rectifier 93 which furnishes current for a printing solenoid 94 which, when energized, actuates the rod 28 to cause the printing operation. The other side of the line is connected in series and in parallel to the contacts 48, 59, 5| and 52 and to a push button 95 having two contacts 96, which is normally closed, and 91, which is normally open. When the push button 95 is depressed, it closes the contact 91 and current passes through a lead 98, a lead 99, the contact 59, a. lead I99, the push button contact 91, a lead I9| and a lead I92 to the cold side of the motor 49 which then starts to rotate. Upon rotation of the motor 49, the cams 45, 46 and 41 begin to turn in a clockwise direction. The movable arm 49 is lifted by a surface I93 of the cam 46 and closes the contact 5i as shown in Fig. IX. The push button 95 may now be released, and current passes through the contact 96 from one side of the line, through the lead I99, the contact 5|, a lead I94 and the lead I92 to form a hold-in circuit for the motor. At the same time, the cam 41 has been revolved sufficiently to lift the link 51 and thus start the pawl 19 nroving in a counterclockwise direction. The pin 18 is thus removed from beneath the surface 83, of the preselecting brake BI, and. the pawl-like portion 84 permitted to engage the edge of the disk I9.

In Fig. IX, the portion 84 is shown engaged in one of the notches I8 to preposition the disk III to prevent the engaging edge of the pawl 19 from striking the corner of the second notch I8 to the left.

- -Fig. X shows the cams still further rotated with the contact 52 closed-as a result-of the engagement of its lower arm on the cam surface I93. Closing of the contact 52 at this timemakes no differencein the operation of the inotorbut merely conditions the circuit for a subsequent change. The pawl 19 hasnow. come into contact with that portion of theedge of the disk I9 which is beyond th square shoulder of the notch I8, the corner of which it would have hit had not the preselecting brake 8| moved the disk I9 slightly in a clockwise directionby the engagement of the pawl-lik portion 84 with the inclined wall of the notch I8 in which it is now seated.

In Fig. XI, the cams have rotated far enough so that the arm 51 has been lifted sufliciently to move the pawl 19 to the left far enough for it to drop in the notch I8 and engage the correct one of the teeth 85 and then move both the disk I9 and the ratchet sector 36 a. suflicient distance to the left to line up the correct type characters. The pawl 19 has come into contact with the limit dog 86 and the cam surface 41 has lifted the link 51 a slight distance further than is necessary to make the pawl 19 contact the limit dog 86, thus compressing the spring 68 in the bell crank 66 and assuring that the pawl 19 has moved to the limit of its stroke. At this point, the contact 48 has been closed by the cam 45 andcurrent' passes from the lead 98, through the lead 99, the contact 48, a lead I to the rectifier 93 and thus the solenoid 94 is energized to cause the printing operation. The cams 45 and 41 are constructed with relation to each other to cause the pawl 19 to be firmly forced against the limit dog 86 and thus move the type characters I1 and 23 to' the correct printing position, before the solenoid 94 is energized.

Fig. XII illustrates the position of the partsimmediately after the printing operation. The cam 45 has rotated far enough to permit the contact 48 to open, de-energizing the solenoid 93. The cam 41 is still holding the link 51 up andthe pawl and associated parts at the limit of their stroke, and the movable arm 49 of the double contact 59, 5| has ridden up on a surface I96 of the cam 45. In the normal operation of the mechanism, the fact that contact 59 is now open will make no difference since the current still passes through the contact 98, the lead I99, the contact 5|, the lead I94 and the lead I92 to the motor.

Fig. XIII illustrates the mechanism in the position which will cause the motor to be substantially slowed down in its operation and to'creep through the remainder of the revolution of the cams in order to prevent the momentum'of the rotating parts from carrying the cams past the rest position which would, of course, start the complete cycle over again. The movable arm 49 of the contact 59, 5| has dropped off the surface I96 of the cam 46 and the contact 5| has now been opened. In this position, the current can no longer reach the motor by passing through the contact 96, the lead I99 and the contact 5| to leads I94 and I92 because the contact 5| is open. Neither can it pass through the contact 96, the lead I99, the contact 59 and the lead 89 because this latter circuit is all on one side'of the line. Therefore, the'contact 52 still being closed, the current will pass through the lead 98, the contact 52, a selenium rectifier I91, a resistance I98 and the lead I92 to the motor. However, the selenium rectifier being in the circuit, the alternating currentwaves are rectified'into intermittent'direct current and this intermittent current energizes the motor only enough to cause it to inch or rotate at a very low speed. Thus for the remainder of the cycle the motor moves relatively much slower than in the first five-sixths of the cycle and when the lower arm of the contact 50 drops off the surface I06 of the cam 46 and the circuit supplying the half wave rectified direct current to the motor is broken, the motor will immediately stop and there will be insufficient momentum to carry the parts beyond the rest pos tion. a

If the push button 95 is not released immediately after the arm 49 is engaged by the cam surface I03, as it should be, but is held in throughout the entire cycle, and the contact 91 is thus closed, at the position illustrated in Fig. XIII, the opening of the contact will not cause the current to fiow through the selenium rect fier circuit. If the button is held in, the current can pass through the lead 98, the lead 99, the contact 50, the lead I00, the contact 91, the lead IOI and the lead I02 to the motor. This would mean that if the button were held in, the motor would not slow down slightly before the position shown in Fig. )HII but would continue at high speed and would start a second selecting and printing cycle. Therefore, the cam surface I06 is necessary to open the contact 50 as shown in Fig. XII. As has been explained, if the button is not held in at this time the opening of the contact 50 has no effect upon the operat on. the push button is held in and the contact 91 is closed, breaking the contact 59 will cause the motor to be immediately slowed down. The current will not pass through the circu t .iust described with the contact 50 open. If the push button is held in, there is no connection through which the current can flow through contact 5I since it will only be connected to one side of the line at the point of contact of the lead IOI and the resistance I08. However, the current can, and will. pass through contact 52 and the selenium rectifier to the motor.

In Fig. XIII, the link 51 has been lowered and the pawl I0 and its associated parts removed from contact with the disk I0 and the ratchet sector 36. The ratchet sector 36, having been released by the pawl I0, has permitted the ratchet lever 34, the arm I9 and the arcuate strip 22 to return to their normal positions.

The embodiment of the invention that has been disclosed may be modified to meet various requirements.

Having described the invention, I claim:

1. In a printing weighing scale having a mripherally notched major-indicia-bearing disk movable in response to loads weighed on said scale, a minor-indicia-bearing member bearing indicia, a lever having a toothed end lying adjacent the edge of said disk and operatively connected to said minor-indicia-bearing member and fixed position means for imprinting the indicia borne by both of said members, a notch engaging pawl movable through a fixed path If, on the other hand,

along the periphery of said disk and engageable in that one of the notches therein positioned in such path in response to a load on said scale and engageable in that one of the teeth in said lever adjacent which such notch in said disk is positioned by such load, a stop for limiting the movement of said pawl after engagement in such notch, linkage drivingly connected to said pawl for moving said pawl through such path, in combination, a preselecting member engageable with the periphery of said disk just prior in time to the engagement of said pawl in one of such notches for moving said disk if such notch is in position to be struck on the edge by said pawl and for holding said disk stationary until such engagement of said pawl, a two speed motor, a manually-operable starting switch for said motor, a cam driven by said motor for operating said linkage, switches for controlling the speed of said motor, a second cam driven by said motor for controlling said switches and another cam driven by said motor for controlling the operation of said printing means, whereby said motor rotates said cams to move said linkage and pawl to move said indicia bearing members until engagement of said pawl with said stop, and to cause imprinting of the indicia on said members and to operate said switches to slow the speed of said motor during the return of said pawl to starting position and then to stop said motor.

2. In a printing weighing scale having a peripherally notched major-indicia-bearing disk movable in response to loads weighed on said scale, a minor-indicia-bearing member, a lever having a toothed end lying adjacent the edge of said disk and operatively connected to said minorindicia-bearing member and fixed position means for imprinting the indicia borne by both of said members, a notch engaging pawl movable through a fixed path along the periphery of said disk and engageable in that one of the notches therein positioned in such path in response to a load on said scale and engageable in that one of the teeth in said lever adjacent which such notch in said disk is positioned by such load, a stop for limiting the movement of said pawl after engagement in such notch and tooth, in combination, linkage drivingly connected to said pawl for moving said pawl through such path, a two speed motor, a manually-operable starting switch for said motor, a cam driven by said motor for operating said linkage, switches for controlling the speed of said motor, a second cam driven by said motor for controlling said switches and another cam driven by said motor for controlling the operation of said printing means, whereby said motor rotates said cams to move said linkage and pawl to move said indicia bearing members until engagement of said pawl with said stop, and to cause imprinting of the indicia on said members and to operate said switches to slow the speed of said motor during the return of said pawl to starting position and then to stop said motor.

LAWRENCE S. WILLIAMS. 

